KR20030087535A - Rotation support structure for dual-bearing reel - Google Patents

Abstract

A rotation support structure for a dual-bearing reel includes a reel unit, a spool shaft, and fluid bearings. The spool shaft is disposed on an inner circumferential side of the reel unit and can rotate relative to the reel unit. The fluid bearings have a plurality of grooves for forming a fluid lubricant film between the reel unit and the spool shaft. The rotation support structure is provided for a high-speed rotation operation of a dual-bearing reel, with which a reduction of the rotation performance during high-speed rotation can be successfully suppressed. <IMAGE>

Description

ROTATION SUPPORT STRUCTURE FOR DUAL-BEARING REEL}

The present invention relates to a support structure, in particular to a rotation support structure of the high-speed rotational portion of both bearing reels.

Dual-bearing reel, in particular, bait A casting casting reel and a motorized reel are mounted with components that rotate at high speed. In the case of bait casting reels, the spool rotates at about 20000 revolutions per minute during casting. In the case of supporting such a high-speed rotating component, a ball bearing, which is a rolling bearing, is conventionally used.

When the ball bearing is used as the supporting structure of the rotating part, there is a slight rotational resistance even in the ball bearing, so that the rotational performance may decrease. For example, when a spool of bait casting reel is supported by a ball bearing, the flight distance may decrease due to rotational resistance during casting. Therefore, conventionally, the contact part which contacts the spool shaft by inner ring is formed. The contact portion has a slight gap between the inner rings of the ball bearing and is formed to have a width smaller than the width of the inner rings. The inner ring and the contact portion are slid during the spool high speed rotation, and are supported by the ball bearings at the contact portion during the low speed rotation.

In the rotational support structure using the conventional ball bearing, since the inner ring and the contact portion slide at high speed rotation, rolling resistance of the inner ring and the rolling element can be ignored, and the reduction in rotational performance can be suppressed as compared with the case where no slip occurs. Can be. However, since a slip occurs between the inner ring and the contact portion at high speed rotation, friction occurs at that portion. For this reason, the rotational loss of some degree also arises by friction loss.

An object of the present invention is to make it possible to suppress a decrease in the rotational performance during high speed rotation in the supporting structure of the high speed rotation part of both bearing reels.

The rotation support structure of both bearing reels according to the first aspect of the invention is a support structure of a high-speed rotation part of both bearing reels, and includes a first part, a second part, and a fluid bearing. It is a component disposed on the inner circumference and rotatable relative to the first component. The fluid bearing is a bearing having fluid lubricating film forming means for forming a fluid lubricating film between both parts.

In the rotation support structure, a fluid bearing for forming a fluid lubricating film between the first part and the second part to support both parts in a non-contact manner is arranged. Here, since the first part and the second part are connected by the fluid bearing, the rotational resistance is smaller than that of the support structure by the ball bearing, and friction between solids does not occur and frictional resistance is also reduced. For this reason, the fall of rotational performance can be suppressed as much as possible. In addition, since the fluid bearing can be formed integrally with the component, no special storage space is required. For this reason, enlargement of both bearing reels can also be prevented.

The rotation support structure of both bearing reels according to the second aspect of the invention further includes a rolling bearing or a sliding bearing disposed between the first component and the second component, in which the fluid bearing is a rolling bearing or It is provided between the inner peripheral surface of the sliding bearing and the outer peripheral surface of the second component. In this case, even if the second part rotates with respect to the rolling bearing or the sliding bearing, the second part is supported by the fluid bearing during the high speed rotation by the rolling bearing or the sliding bearing at the low speed rotation. The fall of rotational performance can be suppressed in the whole rotation area | region at the time of high speed rotation, such as low speed rotation and casting.

The rotation support structure of both bearing reels according to the third aspect is the structure of the first or second aspect, wherein the fluid lubricating film forming means has a plurality of grooves formed on the outer circumferential surface of the second component that rotates with respect to the first component. In this case, by forming a groove in the outer circumferential surface of the second component that rotates with respect to the first component, the stability of the rotation can be improved and the rotational precision can be maintained high.

The rotation support structure of both bearing reels according to the fourth invention is the structure of the invention 2 or 3, wherein the first part is a reel main body of both bearing reels, and the second part is a spool shaft rotatably supported by the reel main body. The fluid bearing is located at least at one end of the spool shaft. In this case, the fall of the rotational performance of the spool which rotates simultaneously with the reel main body at the same time can be suppressed as much as possible, and the reel can be miniaturized.

The rotation support structure of both bearing reels according to the fifth aspect of the invention further includes a rolling bearing or a sliding bearing disposed between the first component and the second component, and the fluid bearing includes a rolling bearing or It is provided between the outer peripheral surface of the sliding bearing and the inner peripheral surface of the first part. In this case, even if the first part rotates with respect to the rolling bearing or the sliding bearing, since the first part is supported by the fluid bearing during the high speed rotation by the rolling bearing or the sliding bearing at the low speed rotation, The fall of rotational performance can be suppressed in the whole rotation area | region at the time of high speed rotation, such as at low speed rotation and casting.

The rotation support structure of both bearing reels according to the sixth aspect is the structure of the first or fifth aspect, wherein the fluid lubricating film forming means has a plurality of grooves formed on the inner circumferential surface of the first component that rotates with respect to the second component. In this case, by forming a groove in the inner circumferential surface of the first component that rotates with respect to the second component, the stability of rotation can be improved and the rotational precision can be maintained high.

The rotation support structure of both bearing reels according to the seventh aspect is the structure of the fifth or sixth aspect, wherein the first component is a spool that rotates with respect to the reel unit of both bearing reels, and the second component is not rotatable to the reel unit. A spool shaft mounted and penetrating the center of the spool, the fluid bearing being disposed at at least one end of the spool. In this case, the fall of the rotational performance of the spool rotating about the spool shaft can be suppressed as much as possible, and the spool and the reel can be miniaturized.

The rotation support structure of both bearing reels according to the eighth aspect further includes a sealing member for sealing a gap between the first component and the second component on at least one side of the fluid bearing in the structure according to any one of the inventions 1 to 7. Equipped. In this case, since the inside of the fluid bearing is sealed by the sealing member, fluctuations in dynamic pressure or static pressure due to foreign matter intrusion can be suppressed, and problems due to foreign matter intrusion can be prevented.

In the rotation support structure of both bearing reels according to the ninth aspect, in the structure of the eighth aspect, the sealing member is a low friction seal. In this case, since the low friction seal with little rotation loss is used for the sealing member, even if the sealing member is attached, the degradation of the rotational performance can be suppressed.

The rotation support structure of both bearing reels of the tenth aspect of the invention is the structure of the nineth aspect of the invention, wherein the low friction sealing is a magnetic seal having a magnetic fluid supported by either of the two parts. In this case, the magnetic sealing using the magnetic fluid can effectively prevent intrusion of foreign matters, and in the case of a fluid bearing using a fluid other than air, the fluid can be supported in addition to the sealing.

The rotation support structure of both bearing reels according to the eleventh aspect is the structure of the nineth aspect, wherein the low friction seal is a water repellent seal having a water repellent membrane layer provided on at least one opposing portion of both parts. In this case, since the sealing member is comprised by the water repellent membrane layer, intrusion of liquids, such as fresh water and seawater, can be prevented especially effectively, and the corrosion resistance of a component becomes easy to maintain.

1 is a perspective view of both bearing reels to which one embodiment of the present invention is applied.

2 is a plan view of FIG. 1.

3 is a plan cross-sectional view of FIG. 1.

4 is an enlarged cross-sectional view of the spool support portion.

5 is a partial cross-sectional view of the fluid bearing support portion.

6 is a partial cross-sectional view of a rotary support portion of another embodiment.

7 is a partial cross-sectional view of a rotating support portion of another embodiment.

* Explanation of the main symbols in the drawings

1: reel body

16: spool shaft

24a, 24b, 124a, 124b: ball bearing

25a, 25b, 125a, 125b: fluid bearing

26a: Dynamic pressure generating groove

33a, 33b: self-sealing

133a: water repellent seal

1 and 2, both bearing reels to which the sealing mechanism according to the embodiment of the present invention is applied are a low profile reel for bait casting. The reel includes a reel main body 1, a handle for spool rotation disposed on the side of the reel main body 1, and a winding spool rotatably and detachably mounted inside the reel main body 1 A spool 12 is provided. On the reel unit 1 side of the handle 2, a star drag 3 for drag adjustment is provided.

The handle 2 is a double-handle type having a plate-shaped handle arm 2a and a handle portion 2b rotatably mounted at both ends of the handle arm 2a. The handle arm 2a is attached to two screws 2e on a base plate 2c fixedly rotatably fixed to the tip of the handle shaft 30 by a nut 2d, as shown in FIG. It is fixed by. This nut 2d is accommodated in the handle arm 2a and is stopped rotating. For this reason, it can be comprised by the smooth surface without the outer surface connection of the handle arm 2a, and it is a structure which a fishing line is hard to get entangled.

As shown in FIG. 3, the reel unit 1 has a frame 5 and a first side cover 6a and a second side cover 6b attached to both sides of the frame 5. Moreover, the reel main body 1 has the front cover 7 which covers the front, and the thumb rest 8 which covers the upper part, as shown to FIG. 1 and FIG. The frame 5 has a pair of side plates 5a and 5b arranged to face each other at a predetermined interval as shown in FIG. 3 and a plurality of connecting portions 5c connecting these side plates 5a and 5b. have. The long attachment angle part 4 is fixed to the lower two connection parts 5c before and after for attaching a reel to fishing rod R. As shown in FIG.

The first side cover 6a is slidably mounted to the frame 5 so as to allow attachment and detachment of the spool 12 and is openable to and open from the frame 5. The second side cover 6b is screwed to the frame 5. The front cover 7 is mounted between the side plates 5a and 5b at the front of the reel unit 1.

In the frame 5, as shown in FIG. 3, the spool 12 arrange | positioned in the direction orthogonal to the fishing rod R, and the level winder mechanism 15 for winding a fishing line uniformly in the spool 12 are shown. And a clutch lever 17 in contact with the thumb in the case of summing. In addition, between the frame 5 and the second side cover 6b, a gear mechanism 18 for transmitting the rotational force from the handle 2 to the spool 12 and the level winder mechanism 15, and the clutch mechanism (13), the clutch engagement release mechanism 19 for performing engagement release of the clutch mechanism 13, and the engagement release control mechanism 20 for controlling engagement release of the clutch mechanism in accordance with the operation of the clutch lever 17. ), The drag mechanism 21, and the casting control mechanism 22 for adjusting the resistance force at the time of rotation of the spool 12 are arranged. Moreover, between the frame 5 and the 1st side cover 6a, at the time of casting A centrifugal brake mechanism 23 for suppressing backlash is disposed.

As shown in FIG. 4, the spool 12 has a plate-shaped flange portion 12a on both sides, and a cylindrical failure body portion 12b between the flange portions 12a. Moreover, the spool 12 has the cylindrical boss part 12c integrally formed in the substantially center part of the inner peripheral side axial direction of the failure trunk | drum 12b, and the spool shaft 16 which penetrates the boss part 12c is carried out. For example, it is fixed so as not to rotate by serration coupling. This fixing method is not limited to serration coupling, and various coupling methods such as key coupling and spline coupling can be used.

The spool shaft 16 penetrates through the side plate 5b and extends outside of the second side cover 6b. The extended end is rotatably supported by the ball bearing 24a and the fluid bearing 25a by the boss portion 6c formed on the second side cover 6b. The other end of the spool shaft 16 is rotatably supported by the ball bearing 24b and the fluid bearing 25b by the brake case 65 (to be described later) in the centrifugal brake mechanism 23. Here, a slight gap is formed between the inner ring of the ball bearings 24a and 24b and the outer circumferential surface of the spool shaft 16, and the fluid bearings 25a and 25b are formed in the gap. The ball bearings 24a and 24b support the spool shaft 16 at a relatively low rotational speed, such as at the time of thread winding, and the fluid bearings 25a, 25b support the spool shaft at a relatively high rotation, such as casting. 16) Magnetically sealed 33a, 33b is arrange | positioned in the axial direction outer side of the ball bearing 24a, and the axial direction inner side of the ball bearing 24b.

As shown in FIG. 5, the fluid bearings 25a and 25b generate dynamic pressure in a radial direction formed on the outer circumferential surface of the bearing mounting portion of the spool shaft 16 so that a lubricating film of air as a fluid is formed on the outer circumferential surface of the spool shaft 16. A dynamic pressure generating groove 26a is formed between the inner circumferential surfaces of the ball bearings 24a and 24b. For example, the dynamic pressure generating groove 26a generates dynamic pressure in a radial direction. It is a zigzag groove of a triangular wave shape, and is formed in a shape that generates dynamic pressure when the spool 12 rotates at a high speed in the unwinding direction. The dynamic pressure generating groove 26a rotatably supports the spool shaft 16 with a gap between the inner rings of the ball bearings 24a and 24b. The dynamic pressure generating groove 26a is formed by a known processing method such as machining such as laser engraving, electrolytic processing using an electrode, or thin film formation processing such as PVD (physical vapor deposition). The processing precision of the fluid bearings 25a and 25b, that is, the processing precision of the inner circumferential surface of the inner ring of the ball bearings 24a and 24b and the outer circumferential surface of the bearing mounting portion of the spool shaft 16 is 5 μm or less, preferably 2 μm or less, more Preferably, by limiting to 1 μm or less, more stable rotational performance can be obtained.

Thus, since the fluid bearings 25a and 25b which can rotatably support the spool shaft 16 in a non-contact manner are provided between the inner ring of the ball bearing 24a and the spool shaft 16, the high speed rotation The fall of rotational performance can be suppressed and the fall of the flight distance at the time of casting can be prevented.

The magnetic seal 33a is a pair of magnetic support rings 34 and 34 fixed to the boss portion 6c at intervals axially from the outside of the ball bearing 24a, and both magnetic support rings ( A ring magnet 35 fitted to 34 is provided, and a magnetic fluid 36 disposed between the magnetic support ring 34 and the spool shaft 16. The magnetic seal 33a supports the magnetic fluid 36 in the magnetic circuit composed of the ring magnet 35, the magnetic support ring 34, and the spool shaft 16 to seal the gap between the spool shaft and the boss portion 6c. do.

A locking ring 37 for positioning the outer ring of the ball bearing 24a is mounted between the inner (left) magnetic support ring 34 and the ball bearing 24a. Moreover, the O ring 38 which seals between the magnetic support ring 34 and the boss | hub part 6c is attached to the axial direction outer side of the outer magnetic support ring 34. As shown in FIG. The magnetic fluid 36 is, for example, a material in which ferromagnetic fine particles of several nm to several ten nm are stably dispersed in a hydrocarbon oil or a fluorine oil-based solvent using a surfactant. Since the self sealing 33a surrounds the spool shaft 16 with a liquid, there is a high sealing property with respect to the gas. In addition, since there is no solid contact at the sealing portion, no dust is generated. In addition, since there is no solid sliding in the sealing portion, the loss torque is small and rotational performance is less likely to decrease.

The magnetic seal 33b has the same configuration as the magnetic seal 33a, and has a pair of magnetic support rings 34 and 34, a ring magnet 35 fitted to both magnetic support rings 34, and a magnetic support ring 34. ) And a magnetic fluid 36 disposed between the spool shaft 16. A locking ring 37 for positioning the outer ring of the ball bearing 24b is mounted between the outer (left) magnetic support ring 34 and the ball bearing 24b. Moreover, the O ring 38 which seals between the magnetic support ring 34 and the brake case 65 is attached to the inner side of the inner magnetic support ring 34.

The right end of the large diameter part 16a of the spool shaft 16 is arrange | positioned at the penetrating part part of the side plate 5b, and the engaging pin 16b which comprises the clutch mechanism 13 is being fixed there. The coupling pin 16b penetrates the large diameter part 16a along the diameter, and the both ends protrude in the radial direction.

The gear mechanism 18 includes a handle shaft 30, a main gear 31 fixed to the handle shaft 30, a cylindrical pinion gear 32 engaged with the main gear 31, and a level winder mechanism. It has a gear 28a connected to it, and a gear 28b that is rotatably fixed to the handle shaft 30 and meshes with the gear 28a. The upper and lower positions of the handle shaft 30 of the gear mechanism 18 are lower than the conventional position because the height of the thumb rest 8 is lowered. For this reason, the lower part of the side plate 5b and the 2nd side cover 6b which accommodate the gear mechanism 18 is located below the lower part of the side plate 5a and the 1st side cover 6a. The tip end portion of the handle shaft 30 is reduced in diameter, and parallel chamfering portions 30a and male thread portions 30b are formed at the large diameter portion and the small diameter portion of the tip portion, respectively.

The base end (left end of FIG. 4) of the handle shaft 30 is supported by the side plate 5b by the bearing 57. An elastic lip seal member 58 is mounted inside the proximal end of the handle shaft 30.

The pinion gear 32 is formed in the outer circumferential portion of the right end side of FIG. 3 and is engaged with the main gear 31, the engagement portion 32b formed on the other end side, and the tooth portion 32a and the engagement portion 32b. Has a neck (32c) formed between. The engaging portion 32b is formed of a concave groove formed along the diameter in the cross section of the pinion gear 32, and is engaged with the engaging pin 16b fixed through the spool shaft 16. The pinion gear 32 is supported by the side plate 5b by the bearing 43. Inside the bearing 43, an elastic lip attachment sealing member 59 is mounted.

Here, when the pinion gear 32 moves outward and the engaging portion 32b and the engaging pin 16b of the spool shaft 16 are separated, the rotational force from the handle shaft 30 is not transmitted to the spool 12. Do not. The clutch mechanism 13 is constituted by the engaging portion 32b and the engaging pin 16b. When the engaging pin 16b and the engaging portion 32b are engaged, the torque is transmitted directly from the pinion gear 32 having a larger diameter than the spool shaft 16 to the spool shaft 16, so that the torsional deformation becomes less. Torque transmission efficiency is improved.

As shown in FIG. 2, the clutch lever 17 is arrange | positioned behind the spool 12 at the rear part between a pair of side plates 5a and 5b. Long holes (not shown) are formed in the side plates 5a and 5b of the frame 5, and the rotation shaft 17a of the clutch lever 17 is rotatably supported by the long holes. For this reason, the clutch lever 17 can also slide up and down along a long hole.

The clutch engagement release mechanism 19 has a clutch yoke 40, as shown in FIG. The clutch yoke 40 is arranged on the outer circumferential side of the spool shaft 16 and is supported by two pins 41 (only one side) so as to be movable in parallel with the axis center of the spool shaft 16. In addition, the spool shaft 16 can be rotated relative to the clutch yoke 40. That is, even if the spool shaft 16 rotates, the clutch yoke 40 does not rotate. In addition, the clutch yoke 40 has an engaging portion 40a that engages the neck 32c of the pinion gear 32 at its central portion. Moreover, at the outer periphery of each pin 41 which supports the clutch yoke 40, the spring 42 is arrange | positioned between the clutch yoke 40 and the 2nd side cover 6b, The clutch yoke 40 is a spring It is always pressurized inward by 42.

With this configuration, in the normal state, the pinion gear 32 is located at the inner clutch engagement position, and the engaging portion 32b and the engagement pin 16b of the spool shaft 16 engage to the clutch on state. On the other hand, when the pinion gear 32 is moved to the outside by the clutch yoke 40, the engagement of the engaging portion 32b and the coupling pin 16b is separated and the clutch is in the off state.

The drag mechanism 21 includes a star drag 3 for adjusting a drag force, a friction plate 45 pressurized by the main gear 31, and a friction plate 45 by a rotation operation of the star drag 3. Has a press plate 46 for pressurizing the main gear 31 with a predetermined force. The star drag 3 is configured to pronounce when rotated.

As shown in FIG. 3, the casting control mechanism 22 includes a plurality of friction plates 51 arranged to sandwich both ends of the spool shaft 16, and the spool shaft 16 by the friction plate 51. It has a braking cap (52) for adjusting the pressing force of the. The friction plate 51 on the right side is mounted in the brake cap 52, and the friction plate 51 on the left side is mounted in the brake case 65.

As shown in FIG. 3, the centrifugal brake mechanism 23 includes a brake case 65 constituting the reel unit 1, a rotation member 66 provided in the brake case 65, and a rotation member 66. It has a sliding element 67 which is disposed at intervals in the circumferential direction and is mounted to be movable in the radial direction. On the inner circumferential surface of the brake case 65, a cylindrical brake liner 65a, which can come into contact with the sliding element 67, is fixed. The brake case 65 is detachably attached to the circular opening 5d formed in the side plate 5a and swings simultaneously with the first side cover 6a.

Next, a method of using the reel will be described.

In a normal state, the clutch yoke 40 is pressed inward (left of FIG. 3) by the spring 42, and thereby the pinion gear 32 is moved to the engaged position. In this state, the engagement portion 32b of the pinion gear 32 and the engagement pin 16b of the spool shaft 16 are engaged with each other and the clutch is turned on, and the rotational force from the handle 2 is handle shaft 30 and the main gear. 31, it is transmitted to the spool 12 via the pinion gear 32 and the spool shaft 16, and the spool 12 rotates in the direction where it feels. At the time of low rotation, such as during the winding of the thread, the spool shaft 16 is supported by the ball bearings 24a and 24b.

In the case of casting, the braking force is adjusted to suppress backlash. Here, for example, it is preferable to adjust the braking force according to the mass of the bait (a fishing tackle). Specifically, when the mass of the bait is large, the braking force is increased, and when it is small, it is reduced. The braking force for suppressing backlash is adjusted by the casting control mechanism 22 or the centrifugal brake mechanism 23.

When the braking force is adjusted, the clutch lever 17 is pushed downward. Here, the clutch lever 17 moves to the downwardly disengaged position along the long hole of the side plates 5a and 5b. By the movement of the clutch lever 17, the clutch yoke 40 moves outward, and the pinion gear 32 coupled to the clutch yoke 40 also moves in the same direction. As a result, the engagement between the engaging portion 32b of the pinion gear 32 and the engaging pin 16b of the spool shaft 16 is separated, and the clutch is turned off. In the clutch off state, rotation from the handle shaft 30 is not transmitted to the spool 12 and the spool shaft 16, and the spool 12 is in a free rotation state. As the clutch off state, if the spool is sloped in the axial direction so that the spool shaft 16 follows the vertical plane while spooling the spool with the thumb that was in the clutch lever 17, the fishing rod is thrown and the bait is thrown and the spool ( 12) rotates, for example, in the unwinding direction at a high speed of 20000 revolutions or more per minute. At the time of the high speed rotation in the unwinding direction, dynamic pressure is generated by the fluid bearings 25a and 25b so that the spool shaft 16 is supported by the fluid bearings 25a and 25b. In this manner, since the spool shaft 16 is supported by the fluid bearings 25a and 25b and sealed by the magnetic seals 33a and 33b, the rotational performance is less likely to be reduced, and the spool 12 is urged. Rotate so as to extend the bait's flight.

In this state, the spool shaft 16 rotates in the unwinding direction by the rotation of the spool 12, and the rotation is transmitted to the rotating member 66. When the rotating member 66 rotates, the sliding element 67 is brought into sliding contact with the brake liner 65a, and the spool 12 is braked by the centrifugal brake mechanism 23. At the same time, the spool shaft 16 can be braked by the casting control mechanism 22 and prevent backlash.

When the fishing gear comes in contact with water, the handle 2 is rotated. Then, the clutch is turned on by a return mechanism (not shown). In this state, for example, the recovery is repeated to wait for the fish to come in contact. When the fish bites the bait, the handle (2) is rotated to wind the fishing line. At this time, it is necessary to adjust the drag force according to the size of the fish. At this time, the drag force is adjusted by rotating the star drag 3 clockwise or counterclockwise.

[Other Examples]

(a) The structure of the fluid bearing of this invention is not limited to the said Example. For example, as shown in FIG. 6, when the spool 112 is rotatably mounted with respect to the spool shaft 116, the fluid bearings 125a, s between the spool shaft 116 and the spool 112 are rotated. 125b) may be mounted. In the embodiment shown in FIG. 6, ball bearings 124a and 124b are attached between the spool shaft 116 and the spool 112. A small gap is formed between the outer ring of the ball bearings 124a and 124b and the inner circumferential surface of the spool 112, and the fluid bearings 125a and 125b are disposed therebetween. Specifically, the dynamic pressure generating grooves 126a and 126b constituting the fluid bearings 125a and 125b are formed at both ends of the inner circumferential surface of the boss portion 112c of the spool 112. 6, the ball bearings 124a and 124b are shown above the spool shaft 116 in the state shown in figure, and the fluid bearing 125a has the ball bearings 124a and 124b below the spool shaft 116. , 125b).

Even in such a configuration, the same effects as in the above embodiment can be obtained.

(b) The bearing is not limited to a ball bearing but may be a sliding bearing such as a rolling bearing or bushing of another form such as a needle bearing or a roller bearing.

(c) In the above embodiment, self-sealing is exemplified as a low friction seal disposed between both parts, but the sealing member is not limited to self-sealing, but a seal capable of preventing intrusion of foreign matter between the parts. Any structure may be sufficient as it is a member. For example, as shown in FIG. 7, the water repellent sealing 133a may be used. The water repellent sealing 133a is a disk-shaped member made of metal or synthetic resin attached to the inner circumferential surface of the boss portion 6c at the opposite portion of the boss portion 6c and the spool shaft 16. The water repellent film layer 133c is formed on the surface and the inner circumferential surface of the water repellent seal 133a opposite to the fluid bearing 25a. The water repellent film layer 133c is, for example, a metal thin film layer impregnated with a silicone resin, a fluororesin, or the like having water repellency. In addition, the water-repellent sealing may be formed integrally with at least one of both parts, not separately.

Moreover, even if it is a contact type thing, as long as it can reduce rotation resistance, such as sealing with a lip, what kind of thing may be sufficient.

(d) Although the fluid bearing using air as the fluid is exemplified in the above embodiment, the fluid may be in any form. For example, a magnetic fluid may be used as the fluid to be used as a sealant, or lubricating oil or the like may be used to further increase rotational performance.

In the case of using a fluid other than such air, fluid outflow prevention means such as a sealing member or a holding member should be disposed at both ends of the fluid bearing to prevent the outflow of the fluid. In the case of the magnetic fluid, the fluid leakage preventing means can be easily configured because the fluid can be held by the magnetic force.

(e) In the above embodiment, a hydrostatic fluid bearing in which a fluid lubrication film is formed by rotation is used, but a hydrostatic fluid bearing in which a fluid lubrication film is formed by supply of fluid from a compressor can also be used.

According to the present invention, since the first part and the second part are connected by the fluid bearing, the rotational resistance is smaller than that of the support structure by the ball bearing, and friction between the solids does not occur, so the frictional resistance is also reduced. For this reason, the fall of rotational performance can be suppressed as much as possible.

Claims (11)

As the supporting structure of the high speed rotation part of both bearing reels, With the first part, A second component disposed on an inner circumferential side of the first component and rotatable relative to the first component; A fluid bearing having fluid lubricating film forming means for forming a fluid lubricating film between the two parts Rotation support structure of both bearing reels having a. The method of claim 1, Further provided with any one of a rolling bearing and a sliding bearing disposed between the first component and the second component, And the fluid bearing is provided between the inner circumferential surface of any one of the rolling bearing and the sliding bearing and the outer circumferential surface of the second component. The method according to claim 1 or 2, And the fluid lubricating film forming means has a plurality of grooves formed on an outer circumferential surface of the second part that rotates with respect to the first part. The method according to claim 2 or 3, The first part is a reel body of the both bearing reels, The second component is a spool shaft rotatably supported by the reel body, Wherein the fluid bearing is disposed at least at one end of the spool shaft. The method of claim 1, Further provided with any one of a rolling bearing and a sliding bearing disposed between the first component and the second component, And the fluid bearing is provided between the outer circumferential surface of any one of the rolling bearing and the sliding bearing and the inner circumferential surface of the first part. The method according to claim 1 or 5, And the fluid lubricating film forming means has a plurality of grooves formed in the inner circumferential surface of the first part that rotates with respect to the second part. The method according to claim 5 or 6, The first part is a spool that rotates with respect to the reel body of the both bearing reels, The second component is a spool shaft rotatably mounted to the reel body and penetrating the center of the spool, Wherein said fluid bearing is disposed at at least one end of said spool. The method according to any one of claims 1 to 7, And at least one side of the fluid bearing further includes a sealing member for sealing a gap between the first component and the second component. The method of claim 8, And the sealing member is a low friction seal. The method of claim 9, And the low friction seal is a magnetic seal having magnetic fluid supported on either one of the parts. The method of claim 9, And the low friction seal is a water repellent seal having a water repellent membrane layer provided on at least one opposing part of the two parts.